Time-setting mechanism for clock movement with perpetual julian date

ABSTRACT

A time-setting mechanism for a clock movement with perpetual Julian date comprising a device for driving a date indicator including driving means for moving forward said indicator by one jump every twenty-four hours. The movement has an adjusting device for automatically moving said indicator by a number of steps taking into account months with 28, 29 or 30 days, said device comprising a rotary cam driven by at least one step every twenty-four hours, said cam having a profile for steering a sensor bringing about: the oscillating movement of a moving mechanism provided with a pawl system for moving forward the date indicator by the required additional number of adjusting steps; and for moving forward said cam by a number of steps equal to the number of said indicator adjusting steps so as to make it move one complete cycle per year.

This invention concerns a mechanism for setting the hour, date, monthand year of a perpetual date calendar movement, which includes at leastdevices for display of the hour, date, month and year. In particular,the invention concerns such a mechanism that allows rapid correction ofthe information on the displays mentioned above.

Perpetual date mechanisms of an exclusively mechanical type aregenerally associated with mechanical movements, and in particular withautomatic timepiece movements whose operation stops either when they arenot manually wound (simple mechanical movement), or when they are notcarried by a user (automatic mechanical movement).

Thus, when watches containing such movements are sold, it is oftennecessary to correct information about time, that is, setting the hour,date, month and possibly the year, since sales are usually made afterstocking the watches in a warehouse for several months after they arereceived from the factory or the wholesaler.

Currently, this correction activity is complicated and is difficult tounderstand both for the uninformed user and the seller. This type ofdifficulty often results in aborting the sale. This correction operationis done by means of the conventional time-setting stem and by acombination of correcting pushing devices, which are active only for aperiod of the day, each indication of the date having its correctingpushing device (date, months, years).

Thus, the goal of this invention is to remedy this disadvantage bysupplying a time-setting mechanism for the date, month and year of aperpetual date movement, whose correction operations may be carried outsimply and quickly, essentially by manipulation of the conventionaltime-setting stem.

To that end, the purpose of this invention is a mechanism for settingtime in a perpetual date timepiece movement which includes a drivingdevice for driving a date display including driving means that canadvance that indicator by jumps once every 24 hours, this movement alsoincluding an adjusting device that allows this indicator to makeadjusting steps to automatically take account of months with 28, 29 or30 days, said device including a rotary cam which is moved at least onestep every 24 hours, this cam having a profile suitable for operating asensor, causing:

on the one hand, the oscillating movement of a mobile assembly with apawl system to make the date display of the required additionaladjusting step or steps advance, and

on the other hand, the advancement of this cam to make it carry out anumber of steps equal to the number of the adjusting steps of thisindicator in order to have it make one complete turn per year,characterized in that it comprises means for disengaging the sensor todisengage it from the profile of that cam, and means for coupling theindicator with that cam, said coupling means being operated by saiddisengaging means which are themselves controlled by a control stem.

Other characteristics and advantages of the invention will becomeapparent from the detailed description which follows, with reference tothe attached drawings which are given only as examples and in which:

FIGS. 1 to 6 are top views of the movement according to the invention,and show the conditions of the movement before (FIGS. 1 and 2), during(FIG. 3) and after (FIGS. 4, 5 and 6) the change of a day, for examplein the middle of a month, such as the 12th, to the next day;

FIGS. 7 to 9 are views similar to FIGS. 1 to 6, but show conditions ofthe movement before (FIG. 7), during (FIG. 8) and after (FIG. 9) thechange of a day at the end of a month with 30 days to the 1st of thenext month;

FIGS. 10 and 11 are views similar to those in FIGS. 7 to 9, but show theconditions of the movement before (FIG. 10) and after (FIG. 11) thechange from the 29th of the month to the first of the following month,for a February month of 28 days (not a leap year);

FIG. 12 is also a top view of the movement according to the invention,shown equipped with a device to display leap years

FIG. 13 is also a top view ef the movement according to the invention,on which the mobile flap system is seen, allowing February months of 29days (leap years) to be taken into account;

FIGS. 14 and 15 show the condition of the movement after the change fromthe 29th to the 30th of the month in a leap year, before (FIG. 14) andafter the change to the first of the following month (FIG. 15),

FIGS. 16 to 19 are views of the top of the movement represented in FIGS.1 to 15, equipped with a rapid time setting mechanism according to theinvention and illustrating the different functions of this mechanism;

FIGS. 20 to 22 are views similar to FIGS. 16 to 19, and show morespecifically the correlation between the normal time setting mechanismand the rapid time setting mechanism;

FIGS. 23 and 24 are top views of the movement and of the mechanismaccording to the invention, but which show only the means for correctingthe days as linked to the time setting stem.

Referring now to FIG. 8, the general principle of a movement intended tobe equipped with the mechanism according to the invention will bedescribed below, this movement being designated by general reference 1.

Movement 1 consists of a perpetual date calendar mechanism, including adate ring 2 that carries date information 4. This information appears ina window 6 of a dial, which is not shown.

The ring 2 is associated with a driving device 8, which consists ofdriving means composed of an elastic arm 10 integrated with a 24-hourwheel, reference The wheel 12 is engaged with a mobile device 14,meshing with an hour cannon wheel 16, which makes one turn in twelvehours.

The elastic arm 10 comprises, at its free end, a hook 18 intended toengage with interior toothing 22 of the date ring 2, in order to make itadvance once every 24 hours, when the hook 18 engages with a tooth ofthis toothing 22.

A jumper spring 24 maintains the date ring 2 in fixed position until thehook 18, made to rotate by the wheel 12, engages on a tooth, for exampleD1, and winds the elastic arm 10 until it overcomes the force of thejumper spring 24 and almost instantaneously moves the date ring 2 by onejump, for the movement from one day to the next.

It should be noted that device 8 is designed so that after changing tothe next day, as explained above, the hook 18 disengages from thetoothing 22 in order to allow, if necessary, an additional advancementof the ring 2 so that it can carry out one or more adjusting steps andto take account of months with less than 31 days, with the aid of anadjustment device which will be described below.

The driving device 8 is a conventional device, which will not bedescribed in detail.

Movement 1 consists of an adjustment device with a rotary cam 26 drivenat least one step every 24 hours and making one complete turn per year.

The cam 26 is guided in rotation, for example on the surface of themovement, by means not shown and it has a profile 28 intended to guide asensor 30.

The sensor 30 controls the oscillating movement of a mobile device 32which is provided with a pawl system 34 intended to make ring 2 advanceby the required adjusting step or steps.

The sensor 30 also controls the advancement of the cam 26 in order tomake it take a number of steps equal to the number of adjusting steps ofthe ring 2.

The cam 26 is driven by a gear train connected to the hour wheel 16.More precisely, the hour cannon wheel 16 (hereafter called the hourwheel) has a pinion 36, which engages with wheel 38 of a first mobileelement. This first mobile element comprises a finger 40 integrated withthe wheel 38. The gearing-down ratio between the pinion 36 and the wheel38 is such that the wheel 38 makes one rotation in 24 hours. The finger40 interacts with the toothing of a wheel 42 with 31 teeth, belonging toa second mobile element whose pinion 44 drives the cam 26.

It will be noted that the finger 40 is positioned on the assembly sothat it makes contact with the toothing of the wheel 42 after thedriving device 8 has allowed ring 2 to jump.

The cam 26 has an annular shape surrounding the mobile assembly 32 andthe driving device 8. The cam 26 and the hour wheel 16 have the sameaxis of rotation R.

The cam 26 has an internal toothing 46 that works together with thepinion 44 to drive this cam in rotation.

The sensor 30, which has the general shape of an anchor, includes afirst arm 48, which rests, under the action of a return spring 50, onthe profile 28 of the cam 26 by a pallet pin 52.

The pallet pin 52, which is in permanent contact with the profile of thecam 26, has a semi-spherical shape and is located in the vicinity of thefree end of the arm 48. This pallet pin 52 is preferably made of asynthetic ruby

The sensor 30 has a second arm 54, which is connected to the first arm48 by a junction piece 56. This second arm 54 is coupled to the mobileassembly 32 by its free end which is fork-shaped 58 and whose teeth areengaged, in the example shown, with a pin 60 that is integrated with themobile assembly 32.

The sensor 30 includes a third arm 62 extending from the junction piece56 essentially in the prolongation of the first arm 48, whose endinteracts with the spring 50 in order to push the pallet pin 52 in thedirection of the profile of the cam 26

To do this, the sensor 30 is set up pivoting by its junction piece 56,via a pivot pin 64, on the movement, tor example on a bottom plate (notshown).

The axis 64 of the sensor 30 is connected to an eccentric 66 that allowsthe final adjustment of the pallet pin 52 in relation to the profile 28of the cam 26.

In the example shown, the sensor 30 and the spring 50 generally extendunder the cam 26.

The mobile assembly 32 is also associated with a mobile lever 68 whichis linked by one of its free ends to the pin 60, this lever 68 beingcontrolled by the sensor 30. The other free end of the lever 68 has atip 70 engaged with a sawtooth wheel 72. This wheel 72 is integratedwith the wheel 44 belonging to the mobile element driving the cam 26.The lever 68 is kept engaged with the wheel 72 through a leaf spring 74,which rests laterally on the back of the tip 70, in a radial directionof the wheel 72.

Furthermore, it will be specified that the wheels 72 and 42, whichbelong to the mobile element driving the cam 26, are kept in positionbetween each step by a jumper 76, actuated by a spring 78.

The assembly 32 has a base plate 80 mounted in rotation around the axisR, around the hour wheel 16. The base plate 80 extends from the centerof the movement in a radial direction toward the ring 2. This plate 80carries the pawl 34, which is mounted in rotation on it by means of apivot 82.

The pawl 34 is composed, on the one hand, of a tip 84 intended to engagewith the toothing 22 of the ring 2 and on the other hand, of an elasticarm 86 which extends to the top of the plate 80. In this example, thearm 86 extends in the direction of the center of the movement.

The pawl 34 also has a spring 88 acting on the tip 84 to make it enterinto the toothing 22 of the ring 2. In the example illustrated, thespring 88 has the general shape of an L which partially surrounds thepivot 82, one branch of which rests against one side of the tip 84,while the other branch rests against a pin 90 integrated with the plate80.

The pin 90 carries a 24-hour wheel, designated 92, that engages with apinion 94 integrated with the hour cannon. The pin 90 also carries aninertial cam 96 that is driven by the wheel 92, this inertial cam 96periodically interacts with the end of the arm 86 to lock it against apin 98 also supported by the base plate 80.

As will be understood from the detailed description of the functioningof the movement, this arrangement consists of a locking system that,every two months, makes it possible to lock the movement of the arm 86of the pawl 34 to interrupt it at the moment of the adjusting jump orjumps. Thus, this locking system, in a first position, maintains the tip84 nearly stationary to ensure that the ring 2 is driven. In a secondposition, this locking system frees the tip 84 to assure its ratchetfunction for the ring 2, when the ring is actuated, in particular by thedriving device 8.

The profile 28 of the cam 26 is composed of five contiguous sectors,designated as I to V, connected to each other by recesses formingnotches E1 to E5. The depth of these notches determines the radialdisplacement of the sensor 30, and particularly the radial displacementof the pallet pin 52 to make the ring 2 carry out the number ofadjusting steps at the end of months having less than 31 days.

The five sectors I to V form continuous ramps R1 to R5 that extend inthe counterclockwise direction, from the bottom of a notch E_(n) to thetop of a following notch E_(n+1), from a first radius to a second radiusgreater than the first.

One of the notches, designated E3, is deeper than the other four notchesE1, E2, E4 and E5, which are of equal depth.

The notches E1, E2, E4 and E5 have depths that allow them to move thesensor 30 to control, via the mobile assembly 32, the displacement ofthe ring 2 by one adjusting step at the end of months with 30 days(April, June, September, November), while the notch E3 has a depth thatallows it to move the sensor 30 to also control, via the mobile assembly32, the displacement of the ring 2 by two or three adjusting steps,respectively at the end of months with 29 and 28 days (February, leapyear and non-leap year).

To this end, the depth of the notch E3 is not constant. It is associatedwith a system 100 capable of varying its depth once every four years.This system 100, seen in FIG. 13, consists of a mobile flap 102 mountedin rotation on the cam 26 by means of a pin 104. The pin 104 carries awheel 106, which makes one turn every four years, this wheel beingactuated on each complete rotation of the cam for a quarter turn. Forthis, the system 100 interacts, once a year, with a fixed finger of themovement, designated 108. Thanks to this arrangement, the mobile flap102 can close the notch E3 once every four years in order to reduce itsdepth. This makes it possible to limit the displacement of the sensor 30so that it only has the ring 2 make two adjusting steps at the end ofthe month of February in leap years.

Furthermore, the mobile flap 102 has a shoulder, which when the mobileflap closes the notch E3 once, lengthens the ramp R3 by a distancecorresponding to a day.

The wheel 106 is maintained in position by an L-shaped jumper 110,mounted in rotation by means of a pivot 112 which is supported by acrown 116, forming a month ring and integrated with the cam 26.

This jumper 110 interacts with a return spring 114 which acts on one ofthe branches of the L so that the other branch enters between two teethof the wheel 106, this second branch having an end provided for thispurpose. Thus, the jumper 110 and its spring 114 turn with cam 26 at therate of one complete turn per year.

FIG. 13 also shows a device for displaying leap years 120, which canadvantageously equip the movement 1.

The device 120 consists of a star 122 carrying a year display hand (notshown), this hand pivoting on the movement 1. The star 122 is maintainedby a jumper spring 124 ensuring the position of the hand. In the exampleshown, the star 122 has eight branches and is driven by two drivingteeth 126 integrated with the cam 26. Thus the star 122 is controlled,once a year, by these two teeth to make a quarter turn at every completerotation of the cam. This display is invaluable for showing leap years.

Referring to FIGS. 1 to 15, the functioning of the movement will bedescribed below.

In FIG. 1 the conventional date drive device is seen at 21:00 hours,that is at the start of its winding to trigger a normal jump, onchanging from the 12th to the 13th of the month.

The hook 18 of the elastic arm 10 hits against a tooth D1 of thetoothing 22. The pallet pin 52 is in the process of going up the rampR5. The inertial cam 96 has not reached the end 86 of the pawl 34. Thetip 84 can thus rise slowly on the side of a tooth D2. The pawl 34 istherefore free and allows either the function of future changing of thedate or a rapid resetting of the date by means of a device that is notdescribed.

Furthermore, the end of finger 40 has not yet, at this time, reached oneof the teeth of the 31-tooth wheel 42.

In FIG. 2, the conventional date driving device is seen at 23:30 hours.The elastic arm 10 of the driving means has continued its windingwithout the ring 2 having moved as yet, it being held by the jumperspring 24. The two 24-hour wheels, designated respectively 38 and 92,have traveled through the complementary angle corresponding to the timethat has elapsed between 21:00 and 23:30, without any other functiontaking place.

In FIG. 3, the conventional date driving device is seen at midnight, thering 2 being ready to jump one step. The hook 18 has made the ring 2advance during the half hour preceding midnight. The jumper spring 24has risen during this short period. It still holds the ring 2.

In FIG. 4, the driving device is seen just after the jump of the ring 2,that is, after the change to the 13th day of the month. The elastic arm10 of the driving means has returned to its shape at rest. The hook 18starts to disengage from the toothing 22 to allow the future rotation ofthe ring 2, at the end of months with less than 31 days.

In FIG. 5 the condition of the movement is seen after theabove-mentioned jump at 2:00 a.m. The hook 18 of the elastic arm 10 iscompletely disengaged from the toothing 22. The end of the finger 40drives a tooth D3 of the 31-day wheel 42, until the moment when thereturn force of the jumper 76 will be overcome by the movement of finger40 and will end the driving function of this wheel 42 through the actionof the spring 78.

The pinion 44, which is integrated with the wheel 42, drives the cam 26in rotation by means of the internal toothing 70 of this cam. Thus, thecam 26 which is integrated with the ring 116 will have taken anadditional step of {fraction (1/372)}nd of a turn in the clockwisedirection, thus causing the pallet pin 52 to rise on the ramp R5, slowlymoving the sensor 30 in the counterclockwise direction, while the sensor30 drives the mobile assembly 32 in its movement.

During this period, the point of the tip 84 has risen against the sideof a tooth D4 of the toothin 22 of the ring 2. The arm 86 has movedangularly around its axis 82, the end of this arm being pushed by theinertial cam 96 and removing the tip 84 from the toothing 22.

The end of the arm 86 moves until the time when, by 24 hour rotation ofthe inertial cam 96, the cam 96 will let the pawl 34 fall again into thetoothing 22, by the effect of the spring 88. During this period, thering 2 is free to turn, particularly from the effect of a rapid settingof the date.

The maximum displacement of the pawl 34 is reached, in thisconfiguration, at about 4:00 a.m., as FIG. 6 shows, presenting at thatmoment the position of the other mobile elements in movement.

FIG. 7 shows the movement under the same conditions as those previouslydescribed for FIG. 3, but this time before the adjusting step of ring 2for the change from the 30th to the 31st of the month, for a 30 daymonth.

During the period that follows, the inertial cam 96 will position itselfin front of the end of the arm 86 to lock it against the pin 98 in orderto immobilize the pawl 34 with respect to the base plate 80. At thattime, the tip 84 of the pawl enters completely into the toothing 22 ofthe ring 2.

At the same time, the articulated lever 68 is moved slowly by the actionof the sensor 30, via the pin 60, to rise on the toothing of the wheel72. The head 70, of this lever, came to settle in the next tooth gap ofwheel 72, through the effect of the spring 74.

It will be noted that the pallet pin 52 remains on the edge of the notchE1 of the cam 26 on the ramp R1.

As in FIGS. 1 to 5, the driving device 8 will be wound and, aroundmidnight, will make the ring 2 turn for the jump from 30 to 31, as seenin FIG. 8.

FIG. 8 shows the movement's position at 2:00 a.m., just before it makesthe adjusting step from the 31st to the 1st.

The hook 18 is completely disengaged from the toothing 2. At this time,the pawl 34, and more particularly its tip 84, is immobilized on thebase plate 80 by the inertial cam 96, and the pallet pill which is onthe edge of the notch E1 is ready to fall into this notch.

The finger 40 then drives the wheel 42 by one step to advance the cam 26by a corresponding step. The advance of the cam 26 leads to the fall ofthe pallet pin 52 into the notch E1, through, the effect of the spring50. In its course, the sensor 30 moves the mobile assembly 32 inrotation, which then advances the ring 2 by one adjusting step, thanksto the tip 84 which is immobilized by the inertial cam 96 (FIG. 9).

It will be noted in this respect that during the adjustment step, theinertia of ring 2 is not controllable, the more so as the energydistributed by the sprint, 50 varies according to its winding, whichitself depends on the depth of the notches E1 to E5. The solution tothis problem consists of locking the pawl 32 by the inertial cam 96, asmentioned above. This locking takes place at the time when the adjustingjump takes place, thus maintaining the tip 84 in the toothing 22 of thering 2.

Thus after the ring 2 advances a step, the preceding tooth D5 hitsagainst the heel of the tip 84, thus preventing the ring 2 fromadvancing an additional step

Furthermore, it will be specified that, given that the inertial cam 96is always turning, the pawl 32 is free for most of the time and inparticular at the time of the traditional change of date at midnight.However, if a rapid change of date should take place at the time whenthe cam is locking the elastic arm 86, particularly between the periodfollowing the traditional jump to midnight and the adjusting jump at theend of the month, the elastic arm 86 has the flexibility necessary topass over one or more teeth of the toothing 22 above the point of thepawl 84.

To comment further on the foregoing, it will be stated that during thesuccessive days of 31-day months, the pallet pin 52 rises progressivelyalong the length of the ramps R1 to R5 of the cam 26. During this coursewhich represents, in the case of the ramp R1, the interval between twomonths, the spring 50 has been progressively stretched by the arm 62 ofthe sensor 30 and has wound the sensor 30 so that it falls into thenotch E1, when the finger 40 will have controlled the displacement ofthe cam 26. When the sensor 30 moves along the ramp R1, it pivots aroundits axis 64 and causes an angular displacement of the mobile assembly32, via the pin 60. When the sensor 30 goes up the ramp R1, it pivots inthe clockwise direction and displaces the mobile assembly 32 angularly.At the time when the pallet pin 52 falls into the notch E1, the sensor30 pivots around its axis 64 in the counterclockwise direction anddisplaces the mobile assembly 32 angularly in the clockwise direction,which makes the ring 2 take the adjusting step required. The tip 84 ofthe pawl 34, which is immobilized by the inertial cam, then pushes thetoothing 22 in the clockwise direction. Simultaneously, the rotationalmovement of the sensor 30 causes the rotation of the wheel 72, bytraction on the lever 68. The wheel 72 being integrated with the pinion44, the traction movement of the lever 68 also causes the rotation ofthe cam 26 with the same adjusting step, so that this cam 26 remains inphase with the periods of the following months.

FIG. 9 shows the condition of the movement after the adjusting step whenchanging, from the 31st to the 1st, at the end of a 30-day month.

At the time of the step, when the sensor falls into the notch E1 thearticulated lever 68 by driving, its head 70 turns the mobile element ofthe wheels 42, 72, and 44 by one step. Thus the pallet pin 52 did notfall directly to the bottom of the notch E1, but at a distance from thevertical wall of the notch E1, this distance corresponding to one day atthe end of a 30-day month.

FIG. 10 and 11 show the condition of the movement before and after thethree adjusting steps, for the change from the 29th to the 1st, at theend of a month of 28 days.

The movement operates in a manner that is identical to what wasdescribed above, except that the number of steps is determined by thedepth of the notch E3. This notch has a depth predetermined so that thedisplacement of the sensor 30 into this notch causes a displacement ofring 2 by three steps, thanks to an angular displacement corresponding,to the mobile assembly.

However, at the end of the month of February in leap years (see FIGS. 14and 15), the notch E3 may be partially obstructed so as to lead to onlya two step displacement of the ring 2, one day later. The obstruction ofthis notch E3 is done at the right time by means of the mechanism 100described above and in particular by the flap 102.

Referring now to FIGS. 16 to 24, the correction mechanism according tothe invention is described.

This mechanism, like the movement 1, is controlled by a conventionalstem 150, which can occupy several axial positions shown in the figuresby P0, P1 and P2.

In the first position P0 (neutral), the stem 150 is used to wind up thespring barrel of the movement (not shown) if it is not equipped with anautomatic winding system.

The condition of the correction mechanism according to the invention inthe P0 position of the stem 150 is shown in FIG. 16. The differentelements forming this mechanism are now described in association withthis figure.

This correction mechanism consists of a setting lever 152 pivoted on themovement and operating together with the stem 150 in the conventionalmanner. One end of this setting lever 152 rests on a plate 154 held, forexample by rivets, to a disengaging device 156 consisting of three arms156 a, 156 b and 156 c.

The disengaging device 156 is mounted pivoting around an axis 158attached, for example, to a bridge, not represented in the drawing. Oneend or head 160 of the arm 156 c enters into a notch 162 of a clutchrocker 164. This is mounted pivoting, by its opposite end, around anaxis 166 also mounted, for example, in a bridge, not shown.

The rocker 164 has a wheel 168 that is mounted for free rotation on acentral post 170 engaged with the rocker 164. The wheel 168 iscontinuously engaged to the wheel 42 of the perpetual date device and inthis position turns freely.

The mechanism also consists of a control star 172 with six branches thatis pivoted on a bottom plate within the circle defined by the date ring2, so that the teeth of this star 172 may operate together with thetoothing 22 of the ring.

The star 172 is integrated with a control pinion 174 with the samenumber of teeth as the star, which carries it and constitutes with it amobile control element. This mobile control element is associated with ajumper spring 176, which allows positioning it so that one of thebranches of the star 172 is always positioned between two teeth of thetoothing 22.

Furthermore, the mechanism includes a return sprint 178 that comes intocontact with a protuberance 180 provided on the rocker 164, this spring178 being attached to the bottom plate of the movement. In this example,the spring 178 has the shape of a thread spring configured as a U.

In the P0 position of the setting lever 150, the spring 178, by itsreturn force, returns the rocker 164 to its initial position at rest andmoves it away from the mobile control element, so that the engagingwheel 168 is disengaged from the control pinion 174.

By the linked connection of the rocker 164 with the disengagement device156, the return force of the spring 178 causes the rotation of thatdevice in the clockwise direction, so that its arm 156 a rests against apin 182.

The sensor 30, and in particular its arm 48, includes a pin 184 whichprojects outside of the plane of the arm 48. The pin 184 is intended toengage with the arm 156 a of the disengagement device 156 in position P1of the stem as will be described below in connection with FIG. 17.

Thus, the arm 156 a may flip between a first position (FIG. 16) in whichit rests against the pin 182 when the stem is in P0 position, and asecond position (FIG. 17) in which it pushes the pin 184 to disengagethe pallet pin 52 from the profile of the cam 26 when the stem 150 is inposition P1.

Furthermore, the articulated lever 68 includes, next to its tip, a pin186 that also projects beyond the plane of the lever. In the P0 positionof the stem, the disengagement device 156 does not interact with the pin184, so that the end of the lever 68 stays engaged with the sawtoothwheel 72. In the P1 position of the stem, the disengagement device 156,which was tipped il the counterclockwise direction, pushes the pin 186to disengage the tip of the level 68 of the toothing of the wheel 72.

FIG. 17 shows the stem 150 in the position P1, which corresponds to theposition that is generally used for setting the date of the day.

In this position, the setting lever 152 was tipped by the movement ofthe stem in the clockwise direction. The end of the setting level 152,resting against a side 188, concave in shape, of the plate 154, thismovement causes tipping, in the counterclockwise direction, of the plate154 and the disengagement device 156 which is integrated with the plate.

In its movement, the arm 156 a of the disengagement device leaves thepin 182 to come and push the pin 184, which is integrated with thesensor 30, to disengage the pallet pin 52 sufficiently from the profileof the cam 26 to allow its rotation in both directions, withoutinterfering, with this pallet pin 52.

In its tipping movement, the sensor 30 drives, with its arm 54, thetipping of the mobile assembly 32 in the counterclockwise direction,this tipping causing the movement of the pawl 34 above the teeth of thetoothing 22 of the ring 2, without driving the ring 2, since the returnforce of the spring 88 is weaker than that of the jumper spring 24.

Thus the mobile assembly 32 will take a non-functional intermediate, butnevertheless well established.

In this position of the tipping of the mobile assembly 32, the pawl 34must be located so that the inertial cam 96, during its rotation over 24hours, always passes beside the end of the elastic arm 86, the tip 84 ofthe pawl 34 being engaged in the toothing 22 of the ring 2, as if thenormal adjusting operation were to take place. This arrangement allowsforward and backward time setting at whatever time the movement isstopped, since the inertial cam 96 always passes behind the end of thearm 86 without displacing it and consequently, without displacing thepawl 34.

The tipping of the disengagement device 156 in the counterclockwisedirection also allows the disengagement of the lever 68, and moreparticularly of the tip 70 of the toothing of the sawtooth wheel 72, inorder to allow rotation of the wheel 72 in both directions, which isconnected to the correction mechanism according to the invention, inposition P1 of the stem.

In order to do this, the arm 156 a of the disengagement device 156presents a rounded side 190, which pushes the pin 186, integrated withthe lever 68, The kinematics of this arrangement are specified so thatthe tip 70 is located in this tipping position outside of the field ofthe toothing of the wheel 72.

The tipping of the disengagement device 156 also causes the tipping ofthe rocker 164 in the clockwise direction by the action of the end 160of the arm 156 c engaged in the notch 162. This displacement of therocker allows the meshing of the engagement wheel 168 with the controlpinion 174 which is integrated with the control star 172 in contact withthe toothing 22 of the ring 2.

FIG. 18 shows the synchronization of the functions of correction,particularly of the rapid date setting, by means of the stem 150 whichis located in the P1 position.

In this position, the advance of the date ring is done by means of awheel 192 integrated in the conventional manner in rotation with thestem 150. This wheel 192 meshes with a sliding pinion 194 integratedwith a rapid correction wheel 196, for example with three pins. Thenumber of pins determines the correction speed of the ring 2 and may befewer or more than three.

This rapid correction wheel 196 is intended to drive the date ring 2 inthe clockwise direction, while the stem 150, in its P1 position isturned in a negative rotation direction symbolized by the arrow SN (FIG.18).

During its rotation, the ring 2 drives the control star 172 with sixbranches in the example shown. At each movement from one tooth of thetoothing 22 there corresponds a movement of one branch of the controlstar 172.

The control pinion 174, integrated with the control star 172, thus alsomakes one sixth of a turn for a step of the date ring. It will be notedthat, in this example, a step of the date ring 2 corresponds to one day.

Given that in P1 position of the stem 150, the control pinion mesheswith the wheel 168 integrated with the rocker 164, the advance of onesixth of a turn of the control pinion 174 drives the advance of a stepof the wheel 168.

The wheel 168 being engaged with the wheel 42, integrated with thesawtooth wheel 72, the advance of its tooth corresponds to the normaldaily advance that the wheels 42 and 72 would have made driven by thefinger 40, which allows the driving of the cam 26 by {fraction(1/372)}nd of a turn by the pinion 44, as described above.

Thanks to this arrangement, at the time of the operation of rapidcorrection, a synchronization function of the movement of the date rinse2 is carried out with the movement of the cam 26.

In this function, the date ring 2 controls the advance of the cam 26,this ring being the leader.

At the time of the rapid correction by means of a corrector such as theone just described, it is common that the operator unintentionallypasses by the day that he wanted to display in the window and displacesthe date ring by one or more days beyond the desired position. With aconventional date device, this error in manipulation is not verybothersome, because the operator only has to give the date ring anadditional turn to find the desired date position.

However, in the case of a perpetual date clock, this error inmanipulation is much more harmful. After such all error, the operatormust turn the stem to pass all the months of the four following years inorder to find the desired date position.

According to the invention, there will be described below particularlyin connection with FIG. 19, a device allowing the elimination of thisdisadvantage.

As will be understood, this device easily allows, at the time of such anerror in manipulation, going back one or more steps to display thedesired date without disturbing the synchronization of the differentelements of the perpetual mechanism.

This device consists of a correction module 200 with a pawl equippedwith a plate 202 that is mounted pivoting on the bottom plate, notshown, around an axis 204. This plate 202 carries a pawl 206 mountedpivoting around an axis 208 projecting from the plate 202.

The plate 202 comprises, in addition, a pin 210 on which there rests aspring 212 integrated with the bottom plate to return the plate to itsinitial position at rest shown in FIG. 18, position in which thecorrection module comes into contact with the head of a pusher 214partially shown in the drawing.

The pawl 206 comprises, at one ends a tip 216 and at a second oppositeend, a post 218 pressed fit within this pawl.

The plate 202 also carries a cylindrical stop 220 on which the pusher214 rests.

The correction module 200 comprises, in addition, a pawl spring 222 thatwinds, on the one hand, around the stop 220 being attached to it and, onthe other hand, around the axis 204 to rest by its free end against thepost 218 which rests against an edge of the plate 202.

FIG. 19 shows the operation of the correction module 200, By applyingpressure on the pusher 214, for example with the aid of a pointed tool,such as the point of a ball point pen, the stop 220 is acted upon,causing the rocking of the plate 202 in the clockwise direction andleads the tip 216 to push a tooth of the wheel 42 in thecounterclockwise direction.

The rotation of this wheel 42 in the counterclockwise direction causesthe displacement by one step of the date rind in the inverse directionby means of the wheel 168, of the control pinion 174 and the controlstar 172 which are connected kinematically in the P1 position of thecontrol stem 150.

The date displayed may therefore be corrected backwards while retainingthe synchronization of the perpetual mechanism with the ring 2, as FIG.21 shows, since the wheel 42, integrated with the pinion 44correspondingly also drives the cam 26 in the inverse direction by{fraction (1/372)}nd of a turn.

By relaxing the pressure on the pusher 214, the return spring 212returns the module 200 to its initial position. During this movement,the tip 216, thanks to the pivoting of the pawl, passes above a tooth ofthe wheel 42 which is kept immobile in position by the jumper 78.

In FIG. 20, the correction mechanism is mounted with the stem 150 drawninto its P2 position. This additional traction of the stem does notinfluence the position of the elements of the mechanism that were justdescribed.

The end of the setting lever 152 has continued its rotation in theclockwise direction, with only the effect of displacing itself along thelength of the concave side 188 of the plate 154, without causing itsadditional displacement or that of the disengagement device 156. Thisresults from the fact that, in this position, the concave side 188 iscentered on the axis of rotation of the setting lever 152.

The complete traction of the stem 150 has the effect of disconnectingthe wheel 192 from the rapid correction wheel 194 which takes anon-functional position.

According to the example shown in the P2 position of the stem, therotation of this stem 1550 in the negative direction SN allows therotation of the hour and minute hands in the clockwise direction. Inthis position, all the functions of the basic movement, of its date andof its perpetual calendar with the rapid date setting, are retained.

The 24-hour wheel 12 carrying, the elastic arm 10 turns in the clockwisedirection in this case by the manual control of the cannon wheel 16 todrive the ring 2 in the clockwise direction. Similarly, the cannon wheel16 also controls the displacement of the finger 40 in thecounterclockwise direction so that it drives the wheel 42 in thecounterclockwise direction to maintain the synchronization of theperpetual date after the normal change of the date.

The wheel 42 drives the displacement of one step of the wheel 168 which,in the P2 position of the stem, is engaged with the control pinion 174.This displacement drives the rotation in the counterclockwise directionof the date ring by one of the branches of the control star 179.

During the normal change of date or of adjustment, the pawl 34 remainsfree to pivot at the time of the displacement of the date ring 2.

FIG. 20 shows the correction mechanism according to the invention in theperiod between midnight and 4:00 a.m., the stem 150 being in the P2position and being rotated in the negative direction. It can be notedthat if the time setting is done during this period, the stop positionof the pawl is such that the end of its arm 86 is driven by the inertialcam 96 during the rotation, so that the tip 84 of the pawl 34 moves awayfrom the field of the toothing 22 of ring 2.

In these conditions, if this position should remain after the rotationof the stem 150 in the negative direction, in the period from midnightto 4:00 a.m., the ring 2 would remain immobile when the mobile assembly32 moves back.

FIG. 22 shows the operation of the time setting, by the rotation of thestem in the positive direction SP. In this case, it is noted that theend on the finger 40 turns in the clockwise direction and that theelastic assembly of this finger 40 allows its displacement in rotationwithout driving the 31-tooth wheel 42 which is kept in position by thejumper 76.

As specified above, for the rotation of the stem in the negativedirection, it is not advisable to set the time between midnight and 4:00a.m. The inertial cam 96 that turns in the counterclockwise directionwill come into contact with the end of the arm 86 of the pawl 34 andblock its operation by ending up against the pin 98.

FIG. 23 shows a day display device 250, consisting of a star with sevenbranches 252 carrying a day display ring not shown in the drawing andmounted in rotation on the bottom plate. In the normal operating, modeof movement 1, this star 252 is driven once a day by a 24-hour wheel,designated 254, provided with an elastic arm 256 having a configurationthat is analogous to the driving wheel 12 of the date ring (FIG. 20).The wheel 254 is continuously engaged with the pinion 36 carried by thehour cannon wheel.

Thus, when the cannon wheel 16 rotates in the clockwise direction, thepinion 36 drives the wheel 254 in the counterclockwise direction, whichin turn drives the star 252 in the clockwise direction, by a hook 258situated at the end of the arm 256. This star is held in position by ajumper spring 260.

Referring also to FIG. 24, a description will now be given of how theday display device 250 can be put into phase with the current time.

In order to do this, the correction mechanism also includes a rockinglever 270 linked to a pivot 272 integrated with the bottom plate.

This lever 270 comprises a swan's-neck first arm 274 whose free end isintended to interact with the star 252 to make it advance by steps. Thelever 270 has a second arm 276 whose free end is intended to interactwith a two-fingered wheel 278, integrated with the wheel 192.

The lever 270 is returned to a position of rest, disengaged from thetoothing of the star 252, by means of a return spring, for example aleaf spring, designated 280, fixed in the bottom plate by a post 282 andby a screw 284.

When the stem is withdrawn into the P1 position, as shown in FIG. 24,and the stem 1550 is put in rotation in the positive direction, wheels192 and 278 are driven in rotation in the clockwise direction,displacing, the rocking, bar 196 into an inactive position, shown in thefigure, in which it is outside of the field of the toothing 22 of thering 2.

Thus, at each half turn of the wheel 278 in the clockwise direction, oneof the fingers rocks the lever 270 and the free end of the arm 274 makesthe star 252 advance by one step, each step representing a day of theweek.

In FIG. 23, it will be noted that the end 258 of the elastic arm 256includes on a side opposite the first face which normally drives thestar 252, a ramp 288 allowing the arm 256 to retract, at the time ofsetting the hands in the negative direction, without involving the star252, the flexibility of the arm 258 being greater than the moment ofmaintenance of the jumper 260.

What is claimed is:
 1. Time setting mechanism of a perpetual date clockmovement (1) which includes a drive device (8) tor driving a dateindicator (2) comprising driving means (10) that can advance saidindicator (2) by a jump once every 24 hours this movement (1) furthercomprising an adjustment device allowing this indicator (2) to makeadjusting steps to take account automatically of months with 28, 29 or30 days, said device including a rotating cam (26) driven by at leastone step every 24 hours, this cam having a profile (28) suitable fordriving a sensor (3) causing: on the one hand, the oscillating movementof a mobile assembly (32) provided with a pawl system (34) to make thedate indicator (2) advance by the additional step or steps required, andon the other hand, the advance of this cam (26) in order to have it makea number of steps equal to the number of adjusting steps of thisindicator (2), in order to make it carry out one complete turn per year,characterized in that it comprises means (156) for disengaging thesensor (30) to disengage it from the profile (28) of that cam (26), andmeans for coupling the indicator with said cam, said coupling means(164) being driven by said disengagement means (156) which arecontrolled by a control stem (150).
 2. Mechanism according to claim 1,characterized in that said disengagement means (156) are driven by asetting lever (152) associated with the stem (150).
 3. A mechanismaccording to one of the claims 1 and 2, characterized in that thecoupling means (164) consists, on the one hand, of a correction star(172) continuously engaged with the indicator (2) and on the other handof a wheel (168) connected to a rocker (164) which is controlled by saiddisengagement means (156), this wheel (168) being continuously engagedwith a mobile element (42, 72) controlling the rotation of the cam (26).4. Mechanism according to claim 1, wherein the disengagement means (156)comprises a device mounted pivoting on the movement and consisting ofthree arms (156 a, 156 b, 156 c).
 5. Mechanism according to claim 4,characterized in that, in a pulled position (P1, P2) of the stem, thefirst arm (156 a) of the device is set to push the sensor (30), thesecond arm (156 b) is set to push an adjusting lever (68) to disengagefrom the toothing (of a wheel of a mobile element (42, 72) controlling,the rotation of the cam (26), and the third arm (156 c) is set tocontrol the coupling system (164).
 6. Mechanism according to claim 5,characterized in that the coupling means (164) consists of a clutchrocker pivoted on the movement by one of its ends, and in that the thirdarm (156 c) includes a head (160) which enters into a notch (162)provided for at the other end of this rocker.
 7. Mechanism according toclaim 1, further comprising a pawl-actuated corrected module (200)provided with a pivoting plate (202) carrying a pawl (206) mountedpivoting around an axis (208) connected to this plat, this pawlincluding a tip (216) capable of pushing a tooth of a wheel of a mobileelement (42, 72) controlling, on the one hand, the rotation of the cam(26) in the counterclockwise direction and on the other hand, therotation of the date ring (2) in the counterclockwise direction, by thecoupling means (164), in a withdrawn position (P1) of the stem (150), inresponse to a pressure exercised by a pusher (214) on this pawl (206).8. Mechanism according to claim 1, further comprising a rocking lever(270) including a first arm (274) set to make a day star (252) advanceby steps and a second arm (276) interacting with a wheel (278) with twofingers engaged with a rocking bar pinion (196) in a withdrawn position(P1) of the stem (150).